EP1707798A1 - Verstellbares Dosierservoventil eines Einspritzventils sowie dessen Verstellungsverfahren - Google Patents

Verstellbares Dosierservoventil eines Einspritzventils sowie dessen Verstellungsverfahren Download PDF

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Publication number
EP1707798A1
EP1707798A1 EP05425151A EP05425151A EP1707798A1 EP 1707798 A1 EP1707798 A1 EP 1707798A1 EP 05425151 A EP05425151 A EP 05425151A EP 05425151 A EP05425151 A EP 05425151A EP 1707798 A1 EP1707798 A1 EP 1707798A1
Authority
EP
European Patent Office
Prior art keywords
servovalve
shim
casing
tightening torque
shutter
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP05425151A
Other languages
English (en)
French (fr)
Other versions
EP1707798B1 (de
Inventor
Mario Ricco
Adriano Gorgoglione
Sisto Luigi De Matthaeis
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Centro Ricerche Fiat SCpA
Original Assignee
Centro Ricerche Fiat SCpA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Centro Ricerche Fiat SCpA filed Critical Centro Ricerche Fiat SCpA
Priority to DE602005021310T priority Critical patent/DE602005021310D1/de
Priority to AT05425151T priority patent/ATE468482T1/de
Priority to EP05425151A priority patent/EP1707798B1/de
Priority to EP05110564A priority patent/EP1707797B1/de
Priority to AT05110564T priority patent/ATE371107T1/de
Priority to DE602005002126T priority patent/DE602005002126T2/de
Priority to US11/357,594 priority patent/US8231105B2/en
Priority to US11/356,638 priority patent/US7458529B2/en
Priority to JP2006045267A priority patent/JP4358831B2/ja
Priority to JP2006045314A priority patent/JP4594251B2/ja
Publication of EP1707798A1 publication Critical patent/EP1707798A1/de
Priority to JP2010046523A priority patent/JP2010180886A/ja
Application granted granted Critical
Publication of EP1707798B1 publication Critical patent/EP1707798B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8053—Fuel injection apparatus manufacture, repair or assembly involving mechanical deformation of the apparatus or parts thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8092—Fuel injection apparatus manufacture, repair or assembly adjusting or calibration

Definitions

  • the present invention relates to an adjustable metering servovalve for an internal combustion engine fuel injector, and to the relative adjustment method.
  • an injector servovalve normally comprises a control chamber for controlling the injector nozzle control rod.
  • the control chamber has an inlet hole communicating with a pressurized-fuel conduit; and a calibrated fuel outlet or delivery hole normally closed by a shutter.
  • the valve body of the servovalve is normally fixed inside the injector casing, and the shutter is controlled by the armature of an electromagnet.
  • the travel or lift of the armature determines both the opening and closing speed of response of the servovalve, and should therefore be as short as possible. The same travel also determines the delivery hole fuel flow section, and should therefore be as large as possible, within the range of the control chamber outlet hole section. As such, the travel of the armature and/or shutter must be adjusted accurately.
  • Servovalves are known, in which the shutter is separate from the armature, the travel of which is defined at one end by the armature arresting against the shutter in the closed position closing the delivery hole.
  • the armature is guided by a sleeve, one end of which defines the stop arresting the armature towards the electromagnet core.
  • the sleeve is fixed inside a cavity in the casing, in such a position with respect to the valve body as to define the armature travel required to open the delivery hole.
  • Armature travel is adjusted using at least one rigid shim located between the sleeve and the electromagnet core to define the air gap of the armature; and at least another rigid shim located between the sleeve and the valve body to define the armature travel.
  • the rigid shims are selectable from classes of calibrated modular shims, and, for technical and economic reasons, may vary by an amount not less than the machining tolerance, e.g. 5 microns. Adjusting armature travel by discrete quantities with a 5 micron tolerance, however, is relatively inaccurate, to the extent of often failing to keep flow of the injector within the strict range demanded by modern internal combustion engines. Adjustment is therefore a complicated job, involving various trial and error attempts, each of which involves disassembling and reassembling part of the injector. In any case, adjustment on one hand requires a long time work of a skilled operator, on the other hand labour involved, it is frequently unsatisfactory on account of the discrete quantity referred to above.
  • EP-A-0 890 730 proposes a servovalve, in which the armature guide sleeve has a relatively bendable flange, and a thread for assembly inside the casing cavity independently of the valve body.
  • the flange position is adjusted discretely using shims within a given range, e.g. of five microns.
  • the flange is subsequently deformed for fine adjustment by screwing the sleeve to a calibrated tightening torque.
  • the shutter is subjected, on the one hand, to axial thrust exerted by the fuel pressure in the control chamber, and, on the other, to the axial thrust of a spring preloaded to overcome the thrust of the fuel pressure when the electromagnet is deenergized.
  • the spring is therefore designed and sized to exert considerable axial thrust, e.g. of around 70 newtons for 1800 bar fuel pressure.
  • a servovalve has recently been proposed in which, as opposed to exerting axial thrust, the pressurized fuel acts radially on the shutter support, so that fuel pressure action on the shutter is substantially balanced, and the action of the spring and the electromagnet may therefore be reduced. Moreover, since the risk of the armature seizing is negligible, the armature may be arrested directly on the electromagnet core, thus eliminating the residual air gap with respect to the core. In this known servovalve, however, travel of the shutter is adjusted using rigid shims, and is therefore adjustable by discrete amounts roughly equal to the machining tolerance, i.e. 5 microns.
  • the object of the invention is to provide an adjustable metering servovalve and relative adjustment method, which are highly reliable, are cheap to implement, and provide for eliminating the drawbacks of known fuel metering servovalves and the known adjustment method.
  • an adjustable metering servovalve as claimed in Claim 1.
  • Number 1 in Figure 1 indicates as a whole a fuel injector (shown partly) of an internal combustion engine, in particular a diesel engine.
  • Injector 1 comprises a hollow body or casing 2 extending along a longitudinal axis 3, and having a lateral inlet 4 connectable to a high-pressure, e.g. roughly 1800 bar, fuel supply conduit.
  • Casing 2 terminates with a nozzle (not shown) communicating with inlet 4 along a conduit 5, and adapted to inject fuel into a relative engine cylinder.
  • Casing 2 defines an axial cavity 6 housing a metering servovalve 7 comprising a valve body 8.
  • Body 8 has an axial hole 9, in which a control rod 10 slides axially in fluidtight manner; and a flange 11 normally resting on a shoulder 12 of cavity 6.
  • Control rod 10 is adapted to control a pin shutter (not shown) in known manner to close and open the fuel injection nozzle.
  • Casing 2 also has another cavity 13 coaxial with axis 3 and housing an actuating device 14, which comprises an electromagnet 15 for controlling a slotted-disk-type armature 16 integral with a sleeve 17.
  • Electromagnet 15 comprises a magnetic core 18 having a pole surface 19 perpendicular to axis 3, and is held in position by a support 20 as explained in detail below.
  • Magnetic core 18 has a cavity 21 coaxial with axis 3 and housing a helical compression spring 22 preloaded to exert thrust on armature 16 in the opposite direction to the attraction exerted by electromagnet 15. More specifically, spring 22 has one end resting on support 20, and the other end acting on armature 16 via a washer 24 comprising a guide block for guiding the end of spring 22.
  • Servovalve 7 comprises a control chamber 23 communicating permanently with inlet 4 via a passage 25 to receive pressurized fuel.
  • Control chamber 23 is bounded axially at one end by rod 10, and at the other by a bottom disk 30 contacting flange 11 of body 8, and has a fuel outlet or drain passage, indicated as a whole by 26, which is symmetrical with respect to axis 3 and comprises a calibrated-section delivery hole 27 formed in disk 30 along axis 3.
  • Outlet passage 26 also comprises a distribution portion 35 formed in a guide body 28 for guiding armature 16 and located in an intermediate axial position between disk 30 and actuating device 14.
  • Body 28 comprises a base 29 gripped axially by a threaded ring nut 31 screwed to an internal thread 32 of casing 2. More specifically, base 29 of body 28 is housed in fluidtight manner inside cavity 6, and is packed in a fixed position with disk 30 and flange 11, which rests axially on shoulder 12. Body 28 comprises a pin or rod 33 projecting from base 29 along axis 3, in the opposite direction to chamber 23, and bounded externally by a cylindrical lateral surface 34 for axially guiding sleeve 17 of armature 16.
  • Rod 33 is formed in one piece with base 29, and has two diametrically opposite radial holes 36 communicating with an axial portion 37 of distribution portion 35 of passage 26, and therefore communicating in fluidtight manner with calibrated delivery hole 27. Holes 36 come out of rod 33 at an axial location adjacent to base 29 and where an annular chamber 38 is formed along lateral surface 34 of rod 33.
  • Sleeve 17 has a cylindrical inner surface 39 fitted in substantially fluidtight manner to lateral surface 34 with a calibrated diametrical clearance, e.g. of less than 4 microns, or via the interposition of sealing members.
  • Sleeve 17 slides axially along surface 34 between a forward limit position and a withdrawn limit position.
  • the forward limit position closes passage 26, and is defined by an end 42 of sleeve 17 arresting against a conical shoulder 43 of body 28; and the withdrawn limit position opens radial holes 36 of passage 26 completely, and is defined by armature 16 arresting against polar surface 19 of core 18.
  • the fuel exerts zero resultant axial thrust on sleeve 17, by virtue of the pressure in chamber 23 acting radially on surface 34; whereas, in the withdrawn limit position, fuel flows from radial holes 36 into a drain or recirculating channel (not shown) through an annular passage 44 between ring nut 31 and sleeve 17, through the slots in armature 16, through cavity 21 in the core, and through an opening in support 20.
  • Annular chamber 38 is opened and closed by a shutter 45 defined by a bottom portion of sleeve 17 adjacent to end 42.
  • Shutter 45 is therefore activated together with armature 16 by energizing electromagnet 15. More specifically, armature 16 moves towards core 18 to open servovalve 7 and drain the fuel, thus causing a fall in fuel pressure in control chamber 23, so that rod 10 translates axially to open and close the injection nozzle.
  • electromagnet 15 When electromagnet 15 is deenergized, spring 22 restores armature 16 to the Figure 1 position, so that shutter 45 closes passage 26 and therefore servovalve 7.
  • one of the two stop members 19, 43 is fixed inside casing 2 with the interposition of at least one shim. More specifically, core 18 of electromagnet 15 is fixed inside cavity 13 of casing 2 by means of a threaded ring nut 40 engaging an annular shoulder 41 of support 20. The lateral surface of support 20 is housed in fluidtight manner inside cavity 13, while the bottom end of support 20 engages an annular shoulder 47 of core 18.
  • Ring nut 40 is screwed to an external thread 46 of casing 2 to a tightening torque ensuring the desired axial position of core 18.
  • Which axial position is defined by at least one shim comprising a ring 48 of appropriate thickness and located between polar surface 19 of core 18 and a shoulder 49 of cavity 13 of casing 2.
  • shim 48 is defined by an annular member, which is elastically bendable or compressible, but of adequate stiffness.
  • Ring nut 40 is designed to screw to a tightening torque ranging, for example, between 15 and 25 N ⁇ m.
  • the shim 48 is such that, with a tightening torque within the above range, a corresponding axial tightening load is produced ensuring an elastic variation of 10 to 15 microns in the thickness or height of shim 48.
  • shim 48 is made of metal, has an L-shaped cross section with at least one portion of the vertical branch of the L inclined, and is deformed elastically predominantly by bending at the join between the two branches of the L, so that the bottom branch of the L remains parallel to shoulder 49.
  • shim 48' has a C-shaped cross section, and is therefore deformed elastically substantially by compression of the vertical branch of the C. Which compression acts on the vertical branch in the form of combined bending and compressive stress, and therefore also produces a certain amount of bending between the two horizontal branches of the C.
  • one shim 48, 48' may advantageously be combined with one or more rigid shims 51, as shown in the Figure 2 variation of the Figure 1 embodiment.
  • Rigid shims 51 may be calibrated and of modular dimensions, and may be selected to minimize deformation of the deformable shim 48, 48'.
  • the travel of shutter 45 of servovalve 7, i.e. the lift of armature 16, may be adjusted by controlling a dimensional parameter, e.g. the distance between polar surface 19 and shoulder 49, or an operating parameter, e.g. the drain flow of servovalve 7, or the opening speed of servovalve 7 and therefore the flow of injector 1.
  • a dimensional parameter e.g. the distance between polar surface 19 and shoulder 49
  • an operating parameter e.g. the drain flow of servovalve 7, or the opening speed of servovalve 7 and therefore the flow of injector 1.
  • shims 48 and 51 or 48' and 51 are selected to first defines a lift of armature 16 which, with a minimum tightening torque, is slightly smaller than the desired lift.
  • the minimum tightening torque may, for example, be 15 N ⁇ m, and at any rate is such as to ensure sufficient friction to prevent loosening of ring nut 40 by thermal and mechanical stress produced by the engine.
  • the resulting lift may, for example, be 2 to 12 microns more than the desired lift.
  • the lift with the minimum tightening torque is then measured using a feeler gauge, while, using a preferably automatic torque wrench, the tightening torque of ring nut 40, and therefore deformation of shim 48, 48', is increased until the feeler gauge reading shows the desired lift. Should the tightening torque reach a predetermined maximum value, e.g. 25 N ⁇ m, without achieving the desired lift, injector 1 must be rejected or reopened to fit preliminary shims 48, 48' and/or 51 of suitable dimensions.
  • a predetermined maximum value e.g. 25 N ⁇ m
  • preliminary shims 48, 48' and/or 51 may be selected of such a size as to produce slightly more than the desired lift with the maximum tightening torque of 25 N ⁇ m.
  • ring nut 40 may be locked, e.g. electrically spot welded, to casing 2 to ensure against ring nut 40 working loose, even by a minimum amount.
  • travel of armature 16 may be adjusted using a method based on another parameter, such as the amount of fuel injected by injector 1 at one or more reference points; in which case, the result is corrected under the control of a feedback control unit and by acting on the tightening torque of ring nut 40.
  • adjustment is therefore made by inserting inside cavity 13 at least one deformable shim 48, 48' together with one or more rigid shims 51, so that, with a predetermined tightening torque of ring nut 40, the value of the selected parameter is greater or less than the desired value.
  • a fine adjustment is made by successive approximations, e.g. by turning ring nut 40 each time by a predetermined angle: in the first case to increase and in the second case to reduce the axial load. After each turn of the ring nut, the corresponding parameter value is measured until a minimum difference is achieved with respect to the desired parameter value. In this way, the travel of shutter 45 can be adjusted to a tolerance of one micron.
  • a first adjustment can be made based on determining the distance between polar surface 19 of core 18 and shoulder 43 of body 28 or shoulder 49 of casing 2. Subsequently, with injector 1 operating in the injection system, a fine adjustment can then be made based on determining the instantaneous flow of injector 1.
  • the travel of armature 16 is adjustable continuously and therefore more accurately; the need for different shim classes is minimized or even eliminated; high-precision machining of the shims and other parts determining lift of the armature, such as the casing, the magnetic core, and the servovalve 7 assembly, is also reduced; the need for electronic control unit software to compensate for any difference between the injectors is also eliminated; and, finally, by virtue of shutter 45 being balanced, on the one hand, armature 16 may be arrested directly on polar surface 19, and, on the other, the axial load required on deformable shim 48, 48' to achieve the desired dimensional variations is reduced.
  • the shim may have a cross section other than those described and illustrated, and in particular any cross section having a portion which is easily and controllably deformable elastically and preferably predominantly bendable, such as an S-, Z- or ⁇ -shaped cross section.
  • end disk 30 of valve body 8 may be formed in one piece with valve body 8; armature 16 may have a thin layer of nonmagnetic material acting as an air gap; and actuator 14 may be a different type, e.g. piezoelectric.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Soil Working Implements (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Nozzles (AREA)
EP05425151A 2005-03-14 2005-03-14 Verstellbares Dosierservoventil eines Einspritzventils sowie dessen Verstellungsverfahren Active EP1707798B1 (de)

Priority Applications (11)

Application Number Priority Date Filing Date Title
DE602005021310T DE602005021310D1 (de) 2005-03-14 2005-03-14 Verstellbares Dosierservoventil eines Einspritzventils sowie dessen Verstellungsverfahren
AT05425151T ATE468482T1 (de) 2005-03-14 2005-03-14 Verstellbares dosierservoventil eines einspritzventils sowie dessen verstellungsverfahren
EP05425151A EP1707798B1 (de) 2005-03-14 2005-03-14 Verstellbares Dosierservoventil eines Einspritzventils sowie dessen Verstellungsverfahren
AT05110564T ATE371107T1 (de) 2005-03-14 2005-11-09 Verstellbares dosierservoventil eines einspritzventils
DE602005002126T DE602005002126T2 (de) 2005-03-14 2005-11-09 Verstellbares Dosierservoventil eines Einspritzventils
EP05110564A EP1707797B1 (de) 2005-03-14 2005-11-09 Verstellbares Dosierservoventil eines Einspritzventils
US11/357,594 US8231105B2 (en) 2005-03-14 2006-02-17 Adjustable metering servovalve for a fuel injector, and relative adjustment method
US11/356,638 US7458529B2 (en) 2005-03-14 2006-02-17 Adjustable metering servovalve for a fuel injector
JP2006045267A JP4358831B2 (ja) 2005-03-14 2006-02-22 燃料インジェクタのための調節可能な絞りサーボバルブとこれに関係した調節方法
JP2006045314A JP4594251B2 (ja) 2005-03-14 2006-02-22 燃料インジェクタのための調節可能な絞り式のサーボバルブ
JP2010046523A JP2010180886A (ja) 2005-03-14 2010-03-03 燃料インジェクタのための調節可能な絞り式のサーボバルブ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05425151A EP1707798B1 (de) 2005-03-14 2005-03-14 Verstellbares Dosierservoventil eines Einspritzventils sowie dessen Verstellungsverfahren

Publications (2)

Publication Number Publication Date
EP1707798A1 true EP1707798A1 (de) 2006-10-04
EP1707798B1 EP1707798B1 (de) 2010-05-19

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Family Applications (1)

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EP05425151A Active EP1707798B1 (de) 2005-03-14 2005-03-14 Verstellbares Dosierservoventil eines Einspritzventils sowie dessen Verstellungsverfahren

Country Status (5)

Country Link
US (1) US8231105B2 (de)
EP (1) EP1707798B1 (de)
JP (1) JP4358831B2 (de)
AT (2) ATE468482T1 (de)
DE (2) DE602005021310D1 (de)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008049671A1 (de) * 2006-10-27 2008-05-02 Robert Bosch Gmbh Kraftstoffinjektor
EP1918568A1 (de) * 2006-10-24 2008-05-07 C.R.F. Societa Consortile per Azioni Magnetdosierventil für ein Brennstoffeinspritzventil
WO2009021864A1 (de) * 2007-08-14 2009-02-19 Robert Bosch Gmbh Steuerventil für einen kraftstoffinjektor
WO2009086996A1 (de) * 2008-01-07 2009-07-16 Robert Bosch Gmbh Kraftstoffinjektor
EP2138707A1 (de) * 2008-06-27 2009-12-30 C.R.F. Società Consortile per Azioni Brennstoffeinspritzvorrichtung mit balanciertem Mess-Servoventil für einen Verbrennungsmotor
EP1845256B1 (de) * 2006-04-11 2010-01-27 C.R.F. Società Consortile per Azioni Kraftstoffinjektor für Verbrennungsmotoren mit einstellbarem Dosierservoventil
EP2218904A1 (de) * 2009-02-16 2010-08-18 C.R.F. Società Consortile per Azioni Verfahren zur Herstellung eines Kraftstoffeinspritzservoventils
EP2218902A1 (de) * 2009-02-16 2010-08-18 C.R.F. Società Consortile per Azioni Verfahren zur Herstellung eines geöffneten / geschlossenen Elements für ausgeglichene Servoventile und Kraftstoffeinspritzer
EP2218901A1 (de) * 2009-02-16 2010-08-18 C.R.F. Società Consortile per Azioni Verfahren zur Herstellung eines geöffneten / geschlossenen Elements für Servoventile und Kraftstoffeinspritzer
WO2010139501A1 (de) * 2009-06-05 2010-12-09 Robert Bosch Gmbh Schaltventil
WO2014067750A1 (de) * 2012-10-31 2014-05-08 Robert Bosch Gmbh Magnetbaugruppe für ein magnetventil
CN103967666A (zh) * 2013-02-04 2014-08-06 辽宁新风企业集团有限公司 一种中孔蓄压式共轨喷油器液力控制器

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006021736A1 (de) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Kraftstoffinjektor mit druckausgeglichenem Steuerventil
DE602007002813D1 (de) * 2007-07-30 2009-11-26 Fiat Ricerche Einspritzdüse mit ausgeglichenem Messservoventil für einen Verbrennungsmotor
ATE487050T1 (de) * 2008-06-27 2010-11-15 Fiat Ricerche Brennstoffeinspritzvorrichtung mit mess- servoventil für einen verbrennungsmotor
EP2138706B1 (de) * 2008-06-27 2010-11-10 C.R.F. Società Consortile per Azioni Kraftstoffeinspritzgerät mit symmetrischem Mess-Servoventil für einen Verbrennungsmotor
US9464613B2 (en) 2008-06-27 2016-10-11 C.R.F. Societa Consortile Per Azioni Fuel injector equipped with a metering servovalve for an internal combustion engine
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EP2436908A1 (de) * 2010-09-30 2012-04-04 Continental Automotive GmbH Ventilanordnung für ein Einspritzventil und Einspritzventil
JP5304861B2 (ja) * 2010-12-17 2013-10-02 株式会社デンソー 燃料噴射装置
JP2014196810A (ja) * 2013-03-29 2014-10-16 株式会社テージーケー ステッピングモータ駆動式の制御弁
DE102013224719A1 (de) * 2013-12-03 2015-06-03 Robert Bosch Gmbh Magnetbaugruppe für ein Magnetventil
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CN114593104B (zh) * 2022-02-17 2023-03-14 成都飞机工业（集团）有限责任公司 一种对伺服阀输出异常压力问题进行分解检查的方法
CN115306600B (zh) * 2022-08-18 2023-12-29 一汽解放汽车有限公司 燃气喷射阀和汽车

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EP1845256B1 (de) * 2006-04-11 2010-01-27 C.R.F. Società Consortile per Azioni Kraftstoffinjektor für Verbrennungsmotoren mit einstellbarem Dosierservoventil
EP1918568A1 (de) * 2006-10-24 2008-05-07 C.R.F. Societa Consortile per Azioni Magnetdosierventil für ein Brennstoffeinspritzventil
US7513445B2 (en) 2006-10-24 2009-04-07 C.R.F. Societa Consortile Per Azioni Metering solenoid valve for a fuel injector
CN101169085B (zh) * 2006-10-24 2010-05-19 C.R.F.社会联合行动公司 用于燃料喷射器的计量电磁阀
WO2008049671A1 (de) * 2006-10-27 2008-05-02 Robert Bosch Gmbh Kraftstoffinjektor
WO2009021864A1 (de) * 2007-08-14 2009-02-19 Robert Bosch Gmbh Steuerventil für einen kraftstoffinjektor
CN101910606B (zh) * 2008-01-07 2013-06-12 罗伯特·博世有限公司 燃料喷射器
WO2009086996A1 (de) * 2008-01-07 2009-07-16 Robert Bosch Gmbh Kraftstoffinjektor
EP2138707A1 (de) * 2008-06-27 2009-12-30 C.R.F. Società Consortile per Azioni Brennstoffeinspritzvorrichtung mit balanciertem Mess-Servoventil für einen Verbrennungsmotor
US8640675B2 (en) 2008-06-27 2014-02-04 C.R.F. Societa Consortile Per Azioni Fuel injector provided with a metering servovalve of a balanced type for an internal-combustion engine
EP2218904A1 (de) * 2009-02-16 2010-08-18 C.R.F. Società Consortile per Azioni Verfahren zur Herstellung eines Kraftstoffeinspritzservoventils
EP2218901A1 (de) * 2009-02-16 2010-08-18 C.R.F. Società Consortile per Azioni Verfahren zur Herstellung eines geöffneten / geschlossenen Elements für Servoventile und Kraftstoffeinspritzer
EP2218902A1 (de) * 2009-02-16 2010-08-18 C.R.F. Società Consortile per Azioni Verfahren zur Herstellung eines geöffneten / geschlossenen Elements für ausgeglichene Servoventile und Kraftstoffeinspritzer
WO2010139501A1 (de) * 2009-06-05 2010-12-09 Robert Bosch Gmbh Schaltventil
CN102803704A (zh) * 2009-06-05 2012-11-28 罗伯特·博世有限公司 分配阀
CN102803704B (zh) * 2009-06-05 2015-08-12 罗伯特·博世有限公司 分配阀
WO2014067750A1 (de) * 2012-10-31 2014-05-08 Robert Bosch Gmbh Magnetbaugruppe für ein magnetventil
CN103967666A (zh) * 2013-02-04 2014-08-06 辽宁新风企业集团有限公司 一种中孔蓄压式共轨喷油器液力控制器

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DE602005021310D1 (de) 2010-07-01
EP1707798B1 (de) 2010-05-19
JP4358831B2 (ja) 2009-11-04
US20060202145A1 (en) 2006-09-14
JP2006258097A (ja) 2006-09-28
US8231105B2 (en) 2012-07-31
DE602005002126D1 (de) 2007-10-04
ATE371107T1 (de) 2007-09-15
DE602005002126T2 (de) 2008-05-21

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